EP3622202A1

EP3622202A1 - Central web concept in an epicyclic gearbox such as a planetary gearbox and equivalent supporting method

Info

Publication number: EP3622202A1
Application number: EP19723325.7A
Authority: EP
Inventors: Mathias Lutz; Christian Kajinski
Original assignee: Hofer Powertrain Innovation GmbH
Current assignee: Hofer Powertrain Innovation GmbH
Priority date: 2018-04-20
Filing date: 2019-04-23
Publication date: 2020-03-18
Also published as: WO2019202159A1

Abstract

The present invention relates to a planetary gearbox and the planet carrier thereof, wherein because of central coupling a first torque and a second torque resulting from torsion of the planet bearing elements on the planet carrier experience at least partial compensation of the torque components which cancel each other out because of favorable merging of the torques, before the torques are led out. It is thereby possible to use a more filigree, e.g. sheet-metal, planet carrier for planetary gearboxes having fairly large torques.

Description

Mittelstegkonzept at a Räderumlaufgetriebe like a

Planetary gear and equivalent support method

The present invention relates to a planetary gear with a planet carrier.

Furthermore, the present invention is concerned with a method of reducing effects that may arise from skewing of elements of a planetary gear.

In other words, the present invention relates to a planet carrier according to the preamble of claim 1 and a method according to the preamble of claim 11.

Technical area

Planetary gear in the form of planetary gears exist in many configurations. Common to the most diverse forms of planetary gears is a certain number of gears, referred to as planets, also referred to as satellites, via one or more stages a force and / or torque transmission between a usually outboard, equipped with a toothed ring gear and a centrally disposed sun gear should be able to. The planets can each be configured in at least two stages. Such planetary gears are also referred to as stepped planetary gears, especially in the cases where the diameter of one part of the planetary gear another, z. B. smaller, diameter than another part of the planetary gear. Of course, it is possible, especially in planetary gears with stepped planetary gears, to arrange a plurality of sun gears, in particular juxtaposed on a central axis of the transmission; It is also possible to arrange a plurality of outer ring gears outside (viewed from a central axis), in particular next to one another.

The planets are often mounted on bolts, more precisely, each planetary gear is on its own bolt. These bolts are positioned in a common mounting manner with their extremities, ie with their left end and with their right end, in a planet carrier. In an area around a center of the respective bolt around is the planetary gear, in particular the stepped planetary gear. The bolt thus carries a planetary gear, in particular a stepped planetary gear. At the same time, the bolt provides an axis of rotation about which the gear can rotate. The support structure, which in particular can rotate about the central axis and carries the bolts or the planets, is usually considered with different names, eg. B. names such as web, cage or planet carrier are common.

FR 2 568 652 A1 (Applicant: Equipements Automobiles Marchal, publication date: 07.02.1986) proposes a satellite carrier or planetary carrier which is constructed with two transverse flanges joined together in the manner of a housing, at least one of which Flanges has longitudinally oriented arms which extend parallel to a central axis. As shown pictorially in one of the figures of FR 2 568 652 A1, the flat, plate-like, one side of the planet carrier forming disc extends parallel to the end face of the three staggered by 120 ° to each other, arranged on bolts planet, being transverse to the Disks extending arms which are bent out of the discs, fasteners are created in the direction of a second, similar plate so that both plates can support them as a flange for the planetary gears of the planetary gear.

DE 10 201 1 101 073 A1 (Applicant: Stöber Antriebstechnik GmbH & Co. KG; Disclosure Date: 08.11.2012) is, inter alia, with a possible further development of a planet carrier, such. B. the known from FR 2 568 652 A1, apart, which should be designed cage-like according to figure description of DE 10 2011 101 073 A1 and should have passages for the planetary gears. The passages are separated by axially extending arms. At a free end of the planet carrier should be provided with an annular disc. Planet pins are mounted with their one end in openings of the annular disc. At another end, the planet pins engage in openings of the planet carrier. As an advantage, the DE 10 201 1 101 073 A1 declares that the planet carrier can be configured as a single-level design of housing and planet carrier, whereby a considerable saving of components should be possible. As a construction of such a planetary carrier looks like, can be very well taken from Figures 2 and 3 of DE 10 2011 101 073 A1. The graphically represented components act as if they were massive, d. have been milled out "from the full".

With regard to possible structures of the individual components and the arrangement between the individual components of the planetary gear, reference is made to the previously cited documents. Instead of explaining the structure of planetary gears in detail, the description of the technical field of the present invention should be used with naming the above-mentioned documents. The disclosures of the aforementioned publications with their references are considered to be fully incorporated herein Invention description incorporated.

State of the art

Depending on the application for a corresponding planetary gear, z. As in the field of drive machines for vehicles, the loads on individual components of the respective planetary gear can be uneven. For this reason, the US 8 647 229 B2 (Applicant: The Timken Company, Publication Date: 11.02.2014), as a more even load distribution in a planetary gear to be possible. As a means of equalizing the load sharing, it is proposed in US 8 647 229 B2 to use a compliant support structure in the planetary gears so that a load can be distributed over two reaction gears. This should make it possible to maintain a parallel gear arrangement at a maximum load application. In addition to drive planet gears, one or more idle planet gears are installed in a corresponding gear. As a result, the uneven load distribution should be avoided.

The idea of keeping non-uniform load distributions via planetary gearboxes as low as possible is promising. However, the solution proposed in US Pat. No. 8 647 229 B2 has a rather complex effect with respect to the movable, in particular rotating parts of the transmission.

DE 1 1 2005 001 867 B4 (patentee: Aisin AW Co., Ltd .; publication date of grant of the patent: 31.03.201 1) also states that in planetary gear units with four sets each consisting of a short pinion and a long pinion on one Scope is difficult to ensure sufficient strength of the bridge section. For this reason, DE 11 2005 001 867 B4 proposes a hub element which should be provided with bridge sections extending from a flange section to a side of the short pinions. By increasing the mass in the interior of the planetary gear thus the desired strength and rigidity to reduce torsion of the carrier should be made.

EP 2 072 863 B1 (proprietors: Gamesa Innovation & Technology, SL et al., Publication date of granting patent: Apr. 25, 2012) proposes to provide a planetary carrier with a rotating plate, the rotating plate being intended to provide support for planetary shafts which extend from both sides of the rotary plate. As a result, it is thus two separate, parallel gearboxes.

A similar construction can be found in CN 107 061 637 A (Applicant: Anhui Science & Technology). Technology; Publication date: 18.08.2017). As can be derived from the figure 4 of the CN 107 061 637 A, two mutually identical plates are arranged parallel to a differently shaped flange plate, between which individual planets can stay in a rotating manner. From the first plate to the second plate and from the second plate to the flange respectively supporting pins on which the planetary gears can rest on the basis of a pin surrounding the recess.

DE 10 2015 217 198 A1 (Applicant: Schaeffler Technologies AG & Co. KG, disclosure date: 09.03.2017) deals with a planetary gear with a stepped planetary gear set, for which an electric motor is provided as a drive unit. The planetary gear should be realized by such Stufenplanetensätze in which the stepped planets are to have different diameters.

In the patent application US 2010/303 626 A1 (Applicant: Vestas Wind Systems A / S; publication date: 02.12.2010) are similar to EP 3 284 976 A1 (Applicant: Flender GmbH, publication date: 21.02.2018) starting from a in the respective publication independently selected state of the art presented several Planetenträgervarianten. But how to design the transmission as a whole is explained in less detail in the documents.

As a thematic focus of the US 2010/303 626 A1 may be considered that a plate of the planet carrier is to be developed so that this plate can replace around the year 2010 known (allegedly) usual plate, which also requires additional plate-like elements for attachment of the planet become. This plate construction is likely to be a tiltably mounted Planetenträgerhalteplatte located between the input plate and planet carrier.

The document EP 3 284 976 A1 initially shows in its description of figures a conventional planetary carrier and furthermore - depending on the count - eight or nine planet carrier in sectional drawings, the input side (in the drawings, the drive side is left) with a double wall construction to form an outer cheek and designed to form an inner cheek. EP 3 284 976 A1 explains that a torsional stiffness can be adjusted by allowing the seats of the planetary axles in the two cheeks to rotate under load the planet carrier cheeks via a variation of the torsional rigidity. In this context, the design could be considered as a torsion spring. US Pat. No. 3,527,121 A (owner: General Motors Corporation, publication of the patent grant: 08.09.1970) shows cage-type planet carriers in two exemplary embodiments, wherein the two exemplary embodiments differ, inter alia, from the transition of a middle plate to the cylindrical housing. The middle plate is enclosed on both sides of the input sun gear on the one side and of the output shaft and the output sun gear on the other side in the first embodiment. From the one level of the introduced torque to the other level of the discharged torque, a so-called "long-pinion" gear, which engages with a so-called "short-pinion" gear, is passed. The "short pinion" gear is supported on the middle plate. In the "short pinion" gear engages the input sun gear. The arrangement is designed asymmetrically with respect to a torque derivation.

The patent application US 2004/259 679 A1 (Applicant: Hispano Suiza, Publication Date: 23.12.2004) - similar to the US 3,527,121 A - a cage-like housing, which has to stiffen against rotation by torques in the region of the planetary bearing arms ,

The German utility model DE 74 01 523 U (owner: Director Nationale des Usines Renault and Automobiles Peugeot, day of publication: 22.05.1975) describes a planet carrier for a planetary gear, which is to be produced by a simple one-piece production of the planet carrier. In this case, essentially radially extending ribs should be present as connecting elements of the planet carrier between three walls. The ribs separate bearing recesses of adjacent pairs of intermeshing planetary gears from each other. A kind of planetary gear is a long, spanning both planes of the planetary gear planetary gear. A second type of planetary gear is a short planetary gear that ends in front of an intermediate wall or center plate. The long planet gear is thus not supported on the intermediate wall. Via an input sun gear, the planetary gear is driven and a reaction sun gear is the output gear. Consequently, a planet carrier is described for a planetary gear, which is equipped with two gear levels and forms a classic connection of sun gear to sun gear. The arrangement is designed asymmetrically with respect to a torque derivation.

The aforementioned documents with their names are incorporated in their entirety into the present invention description. This is to be avoided, no longer and repeatedly discuss well-known relationships between planets, their intervening other gears and the bearings of the gears and components of the transmission, but by reference to the documents as also defined for to be allowed to see the present invention.

From these it can be deduced that planetary gears are often made like a disk.

task

It would be desirable if an arrangement, in particular for stepped planets, would be known in which shearing forces and unequal load distributions can be kept as low as possible by avoiding caused torsions or at least can be reduced. For this it would be good to know a construction.

invention description

The object of the invention is achieved by a planetary gear according to claim 1, a suitable method for avoiding, at least reducing unwanted torsions, can claim 1 1 refer. Advantageous developments can be found in the dependent claims.

One of the components of a planetary gear is a planet carrier. The planet carrier serves to hold individual gears of the planetary gear, in particular to arrange the planet gears locally, d. H. to arrange, for. B. around a sun gear around. As mentioned above, there are different types of planetary gears. There are also different types of planetary gears. One type of planetary gear is based on uniting two adjacent stages through the planets. In particular, it is possible in this case to connect individual partial transmission planes via a, so to speak, bridging planetary gear with one another.

At least one of the planet gears or at least one group or stage, formed from planetary gears, in this case, in an advantageous embodiment, a stepped planetary gear. Step planetary gears are those gears that are composed of two gears of different diameters to a stepped gear.

So that the planetary gears can rotate, z. B. a moment can be transmitted from a sun gear to a ring gear, the planetary gears must be rotatably positioned on bearing assemblies. Particularly favorable for this are wave-like pins, such. B. Bolt. In general, it can be said that each planetary gear has its own planetary bearing element on which the planetary gear can rotate. In addition to a corresponding pin or bolt for this purpose also guide surfaces, ball bearings, spherical bearings, plain bearings or other, rotational movements enabling connections are counted. Simplified may also be said, the gears rotate about or on axes, which are realized by pins, bolts or guide surfaces, optionally in conjunction with ball bearings, roller bearings, plain bearings or other rotation-freedom-offering components.

It is possible to design the pin or the bolt such that it extends from a first carrier disk to a second carrier disk. The support disks may be the limiting, in particular outer, components of the planet carrier. The pin or bolt thus spans the width of the planet carrier. In addition to the pins or bolts holding carrier discs can still be provided an additional discharge plate, the z. B. by covers, one of which may be attached to a support disc, each formed. Another common term for these components of the planetary gear is the term "web", which is implied by the term "web" (in at least some works in the literature) that the web or the support disk rotates again about a frame fixed axis.

The discharge plate is z. B. formed with recesses or omissions such that the pins or bolts have no direct contact with the discharge plate. The pins or bolts extend in an area that is not enclosed by the discharge plate. In one embodiment, it is possible, the deflection inside, d. H. on the inside of the bolts or pins and thus pass more than half of a larger planetary gear.

It can also be said that slopes caused by planets of a planetary gearset can not affect the carrier disks because there is a support structure that provides for a first torque in a first carrier disk and a second torque in a second carrier disk act against each other at least at a center coupling, d. H. at least compensated, if not dissolved. The torque fluxes in the planetary gearboxes are divided. The desired torque flows between the sun gear, planet and ring gear can be used. The undesirable moment fluxes that z. B. build by bevels, are favorably managed and regulate themselves or compensate each other.

In the following, advantageous embodiments and developments are set forth, which in themselves seen, both individually and in combination, can also reveal inventive aspects.

Pins can also be used as pins. The (respective) bolt spans in particular the width of the planet carrier. Preferably, the bolts are held by the carrier disks.

The discharge plate can, for. B. are formed by covers, one of which may be attached to a carrier disk.

The discharge plate is z. B. formed with recesses or omissions such that the pins or bolts have no direct contact with the discharge plate. The pins or bolts may extend in a region that is not enclosed by the discharge plate. As a variant embodiment, it is also possible, the deflector inside, d. H. on the inside of the bolts or pins and thus pass more than half of a larger planetary gear.

If the planet carrier is considered somewhat more abstractly, then it acts like a hollow cylinder, which has individual areas or segments due to its discharge plate. The hollow cylinder can also be referred to as a segmented hollow cylinder. The shell of this hollow cylinder is at least partially broken, in particular, to create space for individual planetary gears. Thus, individual planet gears can extend into the exterior, beyond the mantle or the imaginary mantle of the planet carrier.

The carrier discs are kept at a distance from each other. This is done via arm-like shell sections, in particular a cover. The distance between a carrier disk to its next carrier disk can be adjusted by the height or length of the arms. The arms are slightly longer than the width of the planet gears.

In a particularly advantageous embodiment, a moment of the planet carrier is discharged or deflected via a center of the planet carrier. The carrier disks, which are parts of the planetary carrier, are mounted so that they are uncoupled from an abortive component of a drive train in which the planetary gear is installed, are available. Via a central outlet, an undesired torque or an undesirable torsion can be discharged to a driven component. This is continued via an adapter element. The adapter element can be fastened by bolts. The torque transmission in the planetary gear is advantageously provided so that from a sun gear on a set of larger planet first rotation takes place, from there takes place on a connected to the larger planet second, especially smaller, a planetary torque transmission. Subsequently, a twisting off of the smaller planets, z. B. on a ring gear. The smaller planets can thus mesh with a ring gear.

The present invention can be further developed by the fact that the pins or bolts, which are provided for the planets, are guided laterally past the discharge plate. The bolts are integral and advantageously extend from an outer carrier disk to the other outer carrier disk of the planet carrier.

Due to the material thickness of the carrier disk, each carrier disk has its rigidity. The carrier discs may be designed similar to each other. This makes sense if the stiffness of the first carrier disk and the rigidity of the second carrier disk to each other should be as equal as possible.

If possible, no torsions should occur in the carrier discs. The carrier washers should be connectionless as coupling points for the bolts or pins. Is it possible to make the carrier discs torsionsverwindungsfrei, so can significantly thinner, z. As sheet metal, carrier discs designed or used for the planet carrier.

An introductory torque and an output torque that can be assigned to each individual planet, d. H. it is spoken of several introductory torques and several leading torques at several existing planets, can be guided by a tangential derivative via a bearing seat sleeve so that these moments cancel each other and contribute to Torsionsverwindungsfreiheit the carrier discs.

A coupling, in particular for the discharge of the torsional rigidity or unwanted torsions, can take place at a location which is aligned with a point which is to be found between the teeth of a stepped planet. A torque-related discharge of moments in the carrier disks is possible with the aid of the coupling. A stationary element, such as a connecting plate on a differential following the planetary gear, is possible.

The combinations and embodiments described above can also be in consider numerous other connections and combinations.

A noteworthy component of a planetary gear is the planet carrier itself. The planet carrier is sometimes referred to as a bridge, satellite carrier or cage, with each expression special aspects are brought to the fore. Below is to be spoken by planetary carrier, because the device is intended to carry planets of a planetary gear.

A planetary carrier is provided to locally locate planets of the planetary gear relative to one another and with respect to other components of the planetary gear. The planet carrier is thus the door structure for the planets.

The planets themselves of the transmission can be designed so that the planetary gear is a multi-stage planetary gear. In one embodiment z. B. several planets can be arranged, which engage with each other and thereby, so to speak from planet to planet, generate a multi-stage in the transmission. Another variant, which is also referred to as multistage, consists u. a. to realize a planet with a combination of gears that have different diameters to each other. Such an arrangement is well-known as Stufenplanet or Stufenplanetenrad. It is particularly advantageous if the planet carrier is designed so that it can carry planets of a multi-stage planetary gear. The planet carrier is - in the case - provided as a component of a multi-stage planetary gear.

In a particularly advantageous embodiment, the planet carrier has a first carrier disk and a second carrier disk. The two carrier discs are arranged aligned parallel to each other. Ideally, the carrier discs are round carrier discs, the z. B. are configured annular. The carrier discs may have external dimensions that are substantially equal. So it is z. B. possible to realize the first carrier disk and the second carrier disk, each with an equal largest radius. The carrier discs are flat, circular elements. In other words, in a particularly favorable embodiment, the two carrier disks are annular elements which have an equal maximum radius. This can be done even further by the carrier disks - essentially - have the same masses and the same mass distributions. So it is possible to run the two carrier discs in the end as equal parts.

Each carrier disc serves as a fastening element for receiving a Planet bearing element. Is the planetary gear z. B. to realize with three planets, so ideally three planetary bearing elements are present. Such planetary bearing elements can, for. B. be realized by bolts. In a particularly advantageous embodiment, the ends of the bolts are each fastened to a carrier disk. That is, one end of a bolt terminates in one carrier disk, while the other end of the bolt terminates in the other carrier disk. The first end of the bolt opens into the first carrier disk. The second end of the bolt terminates in the second carrier disk.

If a planetary gear with z. B. five planetary gears or five Stufenplanetenrädern realized so this is preferably vorzuhalten at least five planetary bearing elements. In other words, each planetary gear, in particular each Stufenplanetenrad, has its own planetary bearing element. In one embodiment, the number of planetary gears corresponds to the number of planetary bearing elements. The planetary bearing elements in turn store in the carrier discs. It can also be said that the planet carrier elements are or are attached to these carrier discs. The planetary bearing elements are joined to the carrier disks during assembly of the planetary gear.

In addition to the two carrier discs, there is an adapter element. The adapter element can be decoupled from the carrier discs rotatably move in a different direction than the carrier discs. The carrier discs and the adapter element can rotate with each other. The adapter element is decoupled from the carrier disks. A rotational or rotational movement of the package of carrier discs may be different than a movement of the adapter element.

Preferably, the adapter element is located on the output side of the planetary gear. With the help of the adapter element can be such. B. Torsionsmomente discharged on the output side or reduced or nihilated.

With a construction as previously presented, but also with a corresponding, similar construction, it is possible to derive torsions of the planetary gear, in particular those resulting from inclinations of gears. The planetary gear has a planet carrier. The planet carrier comprises carrier disks. The planet carrier is z. B. configured as previously described. Inclinations that arise on elements that are responsible for the translation of forces and / or torques should, if possible, be reduced, if not avoided, or at least the effects of the inclinations in unwanted torsions. This is z. B. possible with the help of support structures. The torsion or the effect by inclinations in the planetary gear can be discharged via a support structure. For this purpose, a diverting element is provided, the z. B. can be realized in the form of an adapter plate.

Individual moments, in particular torsional moments, can be discharged to a diverting element via the support structures arranged between the carrier disks, in particular in the center. If the diversion element is realized as an adapter plate, further components of a transmission or of a drive can be attached to the diversion element. A metal sheet, which takes over the function of an adapter plate, is characterized among other things by the light, in particular space-saving design.

The carrier disks together with the planetary bearing elements form the holding and positioning structure for the planet gears. Independently of this, there is a second support structure, which opens in particular in the diversion element. The second support structure can realize a different rotation with respect to the first support structure.

Hereinafter, very particularly advantageous embodiments and developments are set forth, which in themselves, both individually and in combination, can again reveal inventive aspects.

In an advantageous embodiment, the adapter element is disc-like. The adapter element could also be referred to as a plate. The adapter element is reminiscent in a favorable embodiment (roughly) to a large soup plate. The adapter element may have an outer, in particular annular, rim, the rim enclosing a central, in particular trough-like, recess.

The preferred installation direction for the individual disks of the planet carrier is a edgewise or transverse to the direction of gravity installation direction (in the sense of an installed mounting direction).

The adapter element is provided so that further elements of the drive train, for. B. further transmission parts of a motor vehicle, are connected.

Another, advantageously present, component is a cover. Each of the at least two existing carrier discs may have their own cover. There is a cover per carrier disk - in this embodiment. The cover can be configured as a tripod, as a four-legged or as a multi-leg. Between the individual legs, z. As the three existing legs of the cover, a free space is provided, which can also be referred to as a gap, can pass through the individual gears of a planetary gear. The cover is time or pavilion-like. The cover can be designed as a flat, pulled down to the sides vault. Ideally, the at least two covers are identical in their dimensions, they can, for. B. differ from each other on the basis of their joining or fastening elements.

From a carrier disk to the next carrier disk spacers may be present, which provide space for individual planes of the planetary gear. In each individual plane of the planetary gear planetary gears levels can be arranged.

In a favorable development, the first carrier disk has a first cover. It is also advantageous if the second carrier disc has a second cover. Thus, there is at least a first cover and a second cover. Each of these covers is also dimensioned so that it creates a distance between the carrier disc and a center plane as a spacer.

The planet carrier may be part of a planetary gear, in particular a planetary gear with stepped planetary. Such a stepped planetary gear may comprise the planet carrier described above.

Another component of the planet carrier is a bearing seat. This bearing seat can be designed Lagerersitzhülsenartig. In such a case, it is also possible to speak of a bearing seat sleeve. The bearing seat sleeve has z. B. a star-shaped ring over which a connection to the bearing seat sleeve receiving adapter element can be made. The bearing seat sleeve is preferably located in a central region of the space, which is provided for receiving gears of the transmission (gear compartment). The bearing seat sleeve is thus between the planets.

The bearing seat should be dimensioned so that it is a bridging element as torque-releasing intermediate member between the cover (or the covers) and the adapter element. In this case, torsions are discharged via the bearing element.

The covers and the carrier discs can by noses and spaces such. B. Recesses or hubs, be coordinated. In such a case, cover and associated carrier disc can be connected by a suitable joining technique. Due to the shape of the cover, but it could also be created by the shape of the carrier disk, a cavity is defined, which spans so that gears of the planetary gear can be accommodated therein (part of the gear housing).

It is particularly advantageous if at least some of the parts, ideally all parts listed below, are designed as deep-drawn and possibly as stamped sheet-metal parts, namely carrier disk, adapter element and cover. In this case, the planet carrier can be produced as a machine-falling part, in which only the individual components have to be joined together. Of course, in particular in an alternative embodiment, individual points may also be joined by welding.

According to an advantageous aspect, it is - thanks to the planetary carrier presented - possible to compensate for uneven distributions of moments and / or forces between particular planetary planets, but also only between simple planets of a planetary gear through central discharge (it should be emphasized that "centered" in the sense is to be understood in a middle range, but is not to be understood as lying exactly in the middle). First, the proposed construction provides a support structure for the planet of a planetary gear. On the other hand, the presented construction offers a support structure for the central discharge or compensation of torsions.

It can also be said that the ends of the bolts or pins or planetary bearing elements are designed as free of torsions as possible at their ends. By attempting to have the least possible torsion at the ends of the bolts, pins, shafts or other planetary bearing elements, it is possible to design the carrier disks as shaped sheet metal parts (instead of, for example, cast-iron parts). When aligning the bolt (it being understood that the term "bolt" also refers to similar components such as pins, shafts or other elongated planetary bearing elements), the play between the bolts should be minimized. In other words, the bolts are arranged as possible without play. Now, if the bearings of the gears arranged in alignment with each other, so the torsional torque introduction can be concentrated on the central region. If a Torsionsmomenteneinbringung focused on the central region of a planetary gear, in particular a stepped planetary gear, so the ends of the bolts, shafts or other support elements for the gears, which is respectively secured to one of the carrier discs, torsionsunbelastastet be added to the carrier disk. A torque discharge can take place over the middle range. It can also be from one Middle web tap be spoken, this Mittelstegabgriff z. B. can be formed by covers. The cover (s) or the center discharge (s) can / can take over both the task of anti-angular components for the gears as well as the task of torsion-conducting components between the carrier discs. A force and torque introduction takes place - in particular thanks to the middle bridge concept - uniformly or parallel on both planets of a planetary gear set (if a stepped planet is installed in the transmission). Thus, the force and torque introduction is evenly distributed to all other components. As a result, an offset between the planetary gear sets and all other components as well as between planet pin bores can be minimized. A burden is distributed more evenly. This arrangement can also be referred to as a parallel connection of the torque transmission, because the bevels or torsion-generating torques of each gear are guided in parallel and in particular advantageously can be performed to cancel each other.

Advantageously, the carrier discs and the adapter element are all the same thickness. All parts can be made as formed sheet metal parts.

Various components or parts of the planet carrier can also be made or assembled by skillful sheet metal forming or by casting into a one-piece part. By combining several parts into a single part of the planet carrier, in particular in one embodiment as a one-piece, z. B. cast planet carrier, on the z. B. bolts for planetary bearing elements are mounted, it is possible to combine several steps in a transmission structure.

In an advantageous embodiment of the invention, the covers are designed as sheet-formed identical parts that can be placed on top of each other and so can be joined. A so designed, constructed of two covers spacers for the carrier discs can also be referred to as a connecting body. In other words, the connecting body is composed of two non-rotatably connected connecting body elements. The individual covers, which may also be referred to as connection body elements, each comprise a base plate element. Here, it is possible that two or more than two connection projections, which may also be referred to as arms or legs, protrude away from the base plate elements in an axial direction, ie, in a direction parallel to the central axis of the cylinder-type planetary carrier. It is particularly advantageous if the connecting projections of a respective connecting body element are each connected to a carrier disk, in particular rotationally fixed. The connection projections can z. B. caulked to a firm connection between Cover and carrier disc manufacture. More generally, by a plastic deformation of the connecting projections, the individual, in particular designed as sheet metal components, connect.

The previously realized by two covers spacing of the carrier discs can also be realized by a sheet metal part from which, in particular, alternately, in two opposite directions, each of which leads a direction on a carrier disc, arms (which can also be referred to as legs) protrude. The arms (or legs) are for connecting the sheet metal part, which provides a single cover with one of the carrier discs.

Due to the momentary relief of the carrier disks or webs, it is possible to make the planet carrier filigree overall. Of course, the individual components such as disk-like carrier plates as a cast component, for. B. as Leichtmetallgussbauteile be made. A measure of the weight saving results from the use of formed sheet metal parts for the individual components of the planet carrier and / or the planetary gear.

The advantageous planetary carrier or the advantageously designed planetary gear can also be described as follows:

The carrier disks, which can also be designed as webs of a planetary gear, are the supporting components for axle-forming components such as bolts, pins, in particular shaft-like pin (s), or guide sleeves (eg, including plain bearings, spherical roller bearings or ball bearings) on which individual Planet gears, z. B. in a particular embodiment, double planets or stepped planets store. Due to the different diameters of the individual planets and due to the moments that are transmitted via the planetary gear, torsions arise at the transitions between the components that implement the support function (s), such as bolts, pins or guide sleeves and the carrier disks or the webs. In this case, a torsion introduced into a first carrier disk or the torque introduced may be larger or smaller than a torsion introduced into a second carrier disk or the second torque introduced. These torsions and moments are derived from the supporting structure of the planetary gear, so its planet carrier.

The torques, torsions and moments that are passed over the first carrier disk, and the torques, torsions and moments that are passed over the second carrier disk can be connected via a connecting the carrier plates component such. B. over a one-piece or multi-part cover, over lateral surfaces or hollow cylinder-like spacers, are brought together so that they compensate each other at least partially. The component into which the moments are introduced from the carrier disks, preferably in opposite directions, may be a connecting component arranged in an outer region or in a middle or inner region of the planetary carrier or of the planetary gear or a connecting assembly. The merged moments, which do not compensate each other, can be forwarded via a center coupling to a further component. This is with center coupling a power and torque leading, z. B. web-like, structure, which does not necessarily have to be arranged completely centrally between two carrier discs, but may also be arranged closer to a carrier disk. The center coupling can be placed in a preferred embodiment in the interior of the planet carrier. The center coupling can lead to a carrier disk towards closer than to the other carrier disk arranged a moment out. The center coupling can also be referred to as a force and / or moment-releasing component.

The center coupling may be placed between the carrier disks such that the torque paths from one carrier disk and from the other carrier disk have different lengths. In this case, the torque path that passes through a carrier disk can be designed by the thickness, strength, rigidity (for example, based on the choice of material) or mass of the carrier disk.

If the discharge takes place via a central region or an inner region of the planet carrier, then the transmission of the forces and / or moments can be guided via a bearing seat sleeve to an adapter element.

Another reason why the position of the center coupling is to be displaced from one side or from a carrier disk (or also from a middle position between the carrier disks) to the other side or towards the other carrier disk lies in the change in the Stiffness of the carrier disk or webs. Depending on the expected moments or the expected torsions one of the webs or one of the planet carrier plates can be made stronger, thicker or more massive than the other planet carrier plate. Will, z. B. due to radii of the gears of the planetary gear, in a planet carrier plate initiated a higher torque than in the other planet carrier plate, it is advantageous if the center coupling is located closer towards the planet carrier plate, which passes through the greater moment. Each of the two plates or carrier discs, which serve laterally, in particular indirectly, as a bearing for the planets, may differ in their stiffness from each other, for. B. due to different thickness of the coats of the plates or carrier discs. About the plates or carrier discs torque flows are forwarded, which are brought together by a connecting the carrier discs component. A location of the merger of the moment fluxes can thus be positioned exactly in a middle between the carrier disks. Because in individual transmissions, especially with stepped planetary gears, the torque distribution within the transmission and thus of the planet carrier is uneven, the moment input or forward conduction in the plates or the planet carrier plates by position of the center decoupling (or center coupling or Mittenausleitung) can be influenced , Figuratively speaking, a center decoupling can be shifted in the direction of one of the sides of the planetary carrier. Particularly preferably, the center decoupling is shifted to the side, in which a stronger torque decoupling seems necessary or necessary. Because the moments are introduced in opposite directions in the decoupling or decoupling component coming from the carrier disks ago, the moments cancel out at least in part again. One of the results of the construction described is a lower twist at the bearings to the planet or the planetary bearing elements out.

According to a further aspect, a cover, a discharge plate or a module connecting the carrier disks can additionally be designed to stiffen the carrier disk. Such stiffening further reduces the torsional effects.

The center coupling can be coupled out to a further component, wherein the further component can be a rotating component or even a stationary component.

There are various possibilities for the storage of the planets. The planets can be mounted on wavy pins. The planets can be mounted on bolts. The planets can be stored on stubs. Also (reverse) ball bearing solutions are possible. The type of planetary bearing element ultimately used depends, among other things, on the requirement for the smooth running of the planets and, if necessary, on the necessity of reducing rotation friction.

Another aspect to be considered is the equal number of bearings or transition points in one planet carrier plate and in the other planet carrier plate. In the case where there are three planetary bearing elements, these are three planetary bearing elements inserted or connected to both in the left planet carrier plate and in the right planet carrier plate. The planetary bearing elements for planets of a type, eg. B. a step or a ring gear, extending from a first, outer, z. B. left, planet carrier plate up to a second, also outer, z. B. right, planet carrier plate.

In the case where wave-like pins are used in the carrier disks as planetary bearing elements, these advantageously extend from one (outer) carrier disk to the other (outer) carrier disk. The existing between the carrier disks structure, eg. The covers or the diverter plate is ideally designed so that it has no contact with the wave-like pins and also no contact with the planet.

The above-described technical solution is particularly effective when a planetary gear is to be used or comes, in which the sun gear is either the drive gear or the output gear, are forwarded through the planetary gear torques. A planetary ring gear (in the sense of an external ring gear) accordingly represents the output gear (if the sun gear is the drive gear) or the drive gear (if the sun gear is the output gear). The planet carrier forms the support structure for the planets in that case as well the support structure for the sun gear and possibly also the support structure for the (outer) ring gear. Such a planet carrier can be stationarily positioned in a transmission. The planet carrier can also be connected to other transmission components continuing, which may also rotate. By way of example, a differential housing may be mentioned. In such an embodiment, the planet carrier goes into a differential case.

The presented technical solution contributes to avoiding, at least reducing, tilting of the planetary axis as much as possible.

The presented technical solution can be realized screw-free in the area of the gearbox interior, more precisely between the carrier disks. In other words, internal gear screws are not present in advantageous embodiments.

Brief Description

The present invention can be better understood by reference to the attached exemplary figures, which set out by way of example particularly advantageous embodiments, without limiting the present invention to these, wherein

FIG. 1 is a schematic representation of a planetary gear according to the invention, FIG. 2 shows a first carrier disk in a 3D view,

FIG. 3 shows a first cover in a 3D view,

FIG. 4 shows a second carrier disk in a plan view,

FIG. 5 shows a second cover in a 3D view,

FIG. 6 shows a bearing seat in a sectional view,

FIG. 7 shows an adapter disk in a 3D view,

FIG. 8 shows a sectional view through an assembled planet carrier, which can be assembled from the components described above into a one-piece component,

Figure 9 shows a further embodiment of a planet carrier, wherein this configuration as a hollow cylindrical, z. B. produced by casting, body is realized,

FIG. 10 shows a further embodiment of a hollow-cylindrical planetary carrier with a center outlet positioned differently compared to FIG. 9,

FIG. 11 is a sectional view of the planet carrier according to FIG. 10 as part of a planetary gear,

FIG. 12 shows a further embodiment of a planetary gear,

FIG. 13 shows the planetary gear according to FIG. 12 together with a differential gear connected thereto,

Figure 14, the transmission, like. FIG. 13, comprising planetary gear and differential gear, together with a ring gear fixed to the planetary gear, FIG.

FIG. 15 shows a sectional view of the gear unit according to FIGS. 12 to 14,

FIG. 16 shows an isometric view of a further embodiment of a planetary gear, in particular a planetary gear with rolling bearings on at least one pin of a planetary carrier,

17 shows an isometric view of the planetary gear according to FIG. 16 from an opposite direction, likewise with a roller bearing in the region of a web, FIG.

FIG. 18 shows a sectional view of the transmission according to FIGS. 16 and 17,

Figure 19 shows another, similar to the embodiment of a planetary gear shown in Figure 18 and

Figure 20 shows a transmission in sectional view, in which as a partial transmission, a planetary gear is integrated according to the previously described embodiments. figure description

Reference numerals from the numerical range of 1 to 199 can be found in the embodiments shown in Figures 1 to 8. The number range from the number 200 to the number 399 is available for reference numerals, which are found in the embodiments of Figure 9 to Figure 11. With numerals from the number 400 and upwards (up to the number 599) reference numerals are used, which treat the jointly discussed figures Figure 12, Figure 13, Figure 14 and Figure 15. Numbers between the number 600 and the number 799 denote reference numerals which deal with Figures 16, 17, 18 discussed in common. Due to the high similarity of the embodiment of Figure 19, the reference numerals between 600 and 799 can also be found in the figure 19. Reference numbers from the reference numeral 800 can be found in FIG.

For reasons of simplification, to promote the readability of the description of the figures and to avoid overburdening of the figures, reference numerals have been omitted in individual figures describing components, components and objects that are also present in other groups of figures, in particular in a similar sense, and there correspondingly by a multiple, multiples of 200 or a factor with the number 200 are presented. In other words, objects, components and components with their reference numerals can be transferred from one embodiment to the other embodiment by adding or subtracting the corresponding one from 200. Thus, the description of the figures can be transferred from one embodiment to another embodiment directly (if necessary adapted by the modified components), without a complete repetition being necessary.

1 shows a schematic representation of a planet carrier 1 ¹ , which is shown in a schematic representation as part of a planetary gear 100. The individual planetary gears, such as the planetary gear 102, are mounted on planetary bearing elements, such as the planetary bearing element 21, to the two carrier disks 3 ¹ , 5 ¹ . More precisely, the ends 27, 29 of the planetary bearing element 21 are inserted in the carrier disks 3 ¹ , 5 ¹ . Finds a skew, z. B. by an inclination of gears instead, so the torsions 150, 152, which may occur in the carrier discs 3 ¹ , 5 ¹ compensated. The resultant 154 of the torsion 150, 152 is significantly reduced. The resultant 154 only has to be discharged via the center outlet 67 'to a further component, such as the differential 108. For this derivation of the moments that arise through a skew, the connection nose 87 is provided as a continuative connection. The first carrier disk 3 shown in FIG. 2 for a planet carrier (see planet carrier 1 in FIG. 8) has a first outer dimension 7, which can also be referred to as a circle diameter. A support collar 13, which has a collar width 15, is arranged around a first central opening 19 of the first carrier disk 3. From the support collar 13 project from a plurality of stop lugs, such as the stop lug 17, radially evenly spaced into the first central opening 19 into it. The first carrier disk 3 has further openings, such as the connection openings 11, 11 ', 11 ", which are provided for fastening a first cover 41 (see FIG. 3) by joining tabs, wherein the tabs fit into the connection openings 11, 1 1 ', 1 1 "can be used. In addition, the first carrier disk 3 has first bolt insertion openings, such as the first bolt insertion opening 28, for fastening a planetary gear (not shown in FIG. Figure 12, see eg Figure 20) serve.

Figure 3 shows the first cover 41 from a bottom view in a 3D oblique view. The first cover 41 is a flat cover made of sheet metal with legs 45, 47, 49 projecting at almost a 90 ° angle thereto. The legs 45, 47, 49 are arranged offset by 120 ° relative to one another. The legs 45, 47, 49 enclose a first center passage 32 as a parallel frame. The first cover 41 is made in sheet metal dimensioned so strong that it can act as a first center outlet 67. The first center outlet 67 has a first connection nose 78, a second connection nose 80 and a third connection nose 82. These flanged connection projections 78, 80, 82 are provided for fastening the second center projection 69 of the second cover 43 (see FIG. 5). At the end of the legs 45, 47, 49 there are a plurality of first connecting lugs, such as the first connecting lug 77 and the second connecting lug 79, via which the cover 41 is connected to the carrier disk 3 or 5 (see FIG. 2 or FIG. 4) can. Between the legs 45, 47, 49, the gap 57 spans. The height of the gap 57 is determined by the height of the middle outlet 67 functioning as a spacer 61. The height of the gap 57 is matched to a width of a planet or a gear half of a planet.

A second carrier disk 5 is shown in Figure 4 in plan view. The second carrier disk 5 has a second outer dimension 9 which is the same size as the first outer dimension 7 of the first carrier disk 3 (see FIG. 2). In the center of the second carrier disk 5 is a second central opening 20. The second carrier disk 5 has three second Bolzeneinführöffnungen, such as the second Bolzeneinführöffnung 30, for receiving bearing pin for planetary gears (not shown in Figure 4). Between the second Bolt insertion openings, such as the second Bolzeneinführöffnung 30, each uniformly spaced a connection opening 12, 12 ¹ , 12 "present, which are provided for attachment of a second cover 43 (see Figure 5).

FIG. 5 shows the second cover 43, which is to be arranged in the installation position in mirror image to the cover 41 (to be seen in FIG. 3). For this reason, the cover 43 has connection openings, such as the first connection opening 84 and the second connection opening 86, into which the first connection nose 78 or the second connection nose 80 of the cover 41 (according to FIG. 3) can engage. The second cover 43 creates a gap 59 by means of its legs 51, 53, 55. The intermediate space 59 is bounded by the legs 51, 53, 55. The length of the legs 51, 53, 55 determines the height of the spacer 63. In the middle of the cover 43 is a center handle 34, which is a recess in the center outlet 69. By means of the connection tabs 81, 83, 85, the cover 43 to the next part, for. B. to the support plate 5 (see Figure 4) are joined.

A trough-shaped part 39 (to be seen in FIG. 6) and an annular part 37 (to be seen in FIG. 7) are components of an adapter element 31 (composed of at least two parts (see reference numbers 31 ', 31 ") (see FIG 6 and 7. The trough-shaped part 39 has a central insert area 40 along the sun axis 6. Axially spaced from the central insert area 40 is an adapter ring insert area 40 'which has a fitting ring 75. The fitting ring 75 is included into the fitting ring 75 ¹ , which surrounds the tray insert opening 38 ^{1 of} the annular part 37 (see Figure 7), more precisely a further trough-shaped part 39 ¹ embedded in the annular part 37. The annular part 37 or the adapter element 31 has an outer diameter 38, which is the same size as the second outer dimension 9 of the second carrier disk 5 (like Figure 4) and in particular the same size as the first outer dimension 7 of the first support plate 3 (like. Figure 2). The diameters, such as the diameter 8 of the trough-shaped part 39 (see FIG. 6), are matched to one another, so that a subsequent installation of the adapter element 31 (see FIG.

In Figure 8, the components shown in Figures 2 to 7 are shown as an assembled planet carrier 1 in a section (in the sense of an assembly drawing), wherein the cross section through the sun axis 6 is placed. The first carrier disk 3 and the second carrier disk 5 have a clearance formed by an overall spacer 65, which is composed of the first cover 41 and the second cover 43. The first cover 41 closes opposite the first carrier disk 3, the first Interspace 57 a. The second cover 43 encloses the second space 59 with respect to the second carrier disk 5. The adapter element 31 projects into the second intermediate space 59 with the annular part 37 and the trough-shaped part 39 attached to the annular part 37. The trough-shaped part 39 forms an annular connection between the annular part 37 and the second cover 43. The adapter element 31 is rotatable about the sun axis 6. The second carrier disk 5 is also rotatable about the sun axis 6. Both parts, adapter element 31 and carrier disk 5 can each decoupled from each other a first rotational movement direction 33 and a second rotational movement direction 35 follow. The directions of rotational movement 33, 35 are indicated in the sectional drawing of FIG. 8 by a symbol for a movement out of the plane of the drawing.

As can also be seen in FIG. 8, part of the adapter element 31 is the bearing seat 71, which is created by the bearing seat sleeve 73. On the bearing seat 71 sits in a rotatable connection created by the cover 41, 43 support structure 89 for the carrier discs 3, 5. The support structure 89 is a double-walled, from the two covers 41, 43 formed reinforcing structure through which the carrier discs 3, 5 stabilized become. Consequently, the carrier discs 3, 5 can be made thinner or filigree.

Figure 9 shows a side view of an embodiment of a planet carrier 201, which is designed as a solid part. The planet carrier 201 is essentially a hollow-cylindrical, two-part, closed by the support disks 203, 205 annular space for receiving planets. The planet carrier 201 has a jacket 292, which is partially broken in a circumferential direction. A jacket portion 294 forms a connection between a first planet carrier plate 202 and a second planet carrier plate 202 '. There are three sheath sections, such as. B. the jacket portion 294, available. The second planet carrier plate 202 'comprises a second carrier disk 205. The first planet carrier plate 202 has a first central opening 219. Radially spaced from the first central opening 219 are located in the first planet carrier plate 202 three Bolzeneinführöffnungen, as the first Bolzeneinführöffnung 228. The three Bolzeneinführöffnungen are evenly distributed (angular distance between them each 120 ° (because 360 ° divided by the number of bolts)), and although they are located on the corner positions of an equilateral triangle which can be placed over the first central opening 219 as a construction aid. A second bolt insertion opening 230, which extends through the second carrier disk 205 and thus through the planet carrier plate 202 ', is arranged opposite or in alignment with the first bolt insertion opening 228. The first planet carrier plate 202 has a disc-like part, the first carrier disc 203. The planet carrier plate 202 has a collar with a collar 215 around the first central opening 219 around. The second planet carrier plate 202 ¹ has a second central opening 220, which is opposite or in alignment with the first central opening 219. In the interior of the jacket 292, a first central outlet 267 leads away from the jacket 292. Moments acting on the bolt insertion apertures 228, 230 may be discharged along the planar support plates 202, 202 ¹ and the diverter plates, such as the diverter plate 296, via the center outlet 267 in a direction toward a center. Around the center lies the trough-shaped part 239. The center outlets 267, 269 open into the trough-shaped part 239. Individual jacket sections 294 are connected via the central outlets 267, 269 with the trough-shaped part 239. Moments which are introduced at the bolt insertion openings 238, 230 into the carrier disks 203, 205 are guided via the jacket sections 294 to the center outlets 267, 269. The diverter plate 296 can be reduced to thin webs as Mittenausleitungen 267, 269 thanks to the solid design (compared with the embodiment of Figures 2 to 8). The jacket sections 294, the center outlets 267, 269 and the trough-shaped part 239 form a (rib-like) discharge plate 296 for discharging torsions and moments from the support disks 203, 205. The center outlets 267, 269 are connected with their web-like or rod-like connections between the Sheath 292 and the trough-shaped part 239 disposed at half position along the spacer 265. In other words, the center outlets 267, 269 are centered between the

Planet carrier plates 203, 205. The length of the spacer 265 corresponds to the length of the shell portions 294th

The planet carrier 201 'shown in FIG. 10 is similar to the planet carrier 201 from FIG. 9, it can also be said that the two planet carriers 201', 201 are almost identical. The description of the planetary carrier 201 shown in FIG. 9 applies, with the exception of the center outlets 267 ', 269' located elsewhere, also to the planet carrier 201 ¹ according to FIG. 10; It can therefore be transmitted directly and should not be repeated at this point, but should be included by referencing at this point. FIG. 11 is the sectional illustration of planet carrier 201 'belonging to FIG. Both figures Figure 10 and 11 can therefore be presented together.

For receiving the sun gear 311, which surrounds the sun shaft 206 as a hollow body, in the planet carrier 201 ¹ as recesses the first central opening 219 and the second central opening 220 on the sun axis 206 are lying centrally in the planetary carrier plates 202, 202 "is available. The support discs 203 205 are over the mantle 292 with his Shroud sections 294 spaced so that on the planetary bearing element 221, the gears such as the larger planet 303 and the smaller planet 304 juxtaposed between the planet carrier plates 202, 202 "fit., So that the planetary bearing elements 221 are each connected at one end firmly to the carrier discs 203, 205 can, the carrier disks 203, 205 each have a plurality, similar to each other

Bolzeneinführöffnungen 228, 230, whose diameter to the diameter of

Planetary bearing element 221 is tuned. By fitting the planetary bearing elements 221, a torque-transmitting connection is produced between planetary bearing element 221 and planet carrier plates 202, 202 ".These transmitted moments resulting from torsions of the planetary bearing elements 221 are conducted via the jacket sections 294 through the diverter plate 296 'into the trough-shaped part 239'. dissipated.

When looking at FIG. 10 with FIG. 11, it is particularly easy to see that the center outlet 267 'is arranged closer to the carrier disk 205, which marks the one end of the planet carrier 201 ^{1 in} addition to the smaller planet 304.

The planetary gear 300 with its planet carrier 201 ¹ is designed for driving from the sun gear 311 via the planet 303, 304 to the ring gear 312.

The collar width 215 of the collar about the central opening 219 corresponds to the outer edge of the first bearing 320. The planet carrier 201 ¹ supports not only the first bearing 320 but also the second bearing 326. The second bearing 326 is a rolling bearing between the sun gear 311 and the bearing seat sleeve 273, in which the moments in the planet carrier 201 ¹ via the center outlets 267 ¹ , 269 'are discharged.

Another example of a planetary carrier 401 is shown in FIGS. 12 to 15. Figure 12 shows the planetary carrier 401 with its planetary gears 502, 506, which are stepped planetary gears. Such a planetary gear 502 is composed of a larger planet 503 and a smaller planet 504. In FIG. 13, the planetary gear 500 is shown together with the differential 508. In Figure 14, the planetary gear 500 is shown with the differential 508 and with the ring gear 512. A sectional view of the two partial transmission planetary gear 500 and differential 508 can be taken from the figure 15. Because the 3D views of the planetary gear 500 shown in FIGS. 12 to 15 show the planetary gear 500 in different degrees of complexity, to which the sectional view of FIG. 15 belongs in addition, FIGS. 12 to 15 can be treated simultaneously. Between two jacket portions of the planetary carrier 401, which is also the first

Sheath portion 494 and second shell portion 494 ¹ can be designated, a stepped planetary gear 506 is inserted into the planetary carrier 401. Adjacent to the first stepped planetary gear 502, there is a first skirt portion 494. Adjacent to a second stepped planetary gear 506, there is a second skirt portion 494 '. The stepped planetary gears 502, 506 each include a larger planet, such as the larger planet 503, and a smaller planet, such as the smaller planets 504, that are non-rotatably coupled together. The first stepped planetary gear 502 is rotatably supported on a first planetary bearing member 421. Other stepped planet wheels 506 are supported accordingly. The first planetary bearing member 421 is in the second

Bolzeneinführöffnung 430 of the planet carrier 401 used and extends from the first planet carrier plate 402 to the second planet carrier plate 402 '. Part of the first

Planet carrier plate 402 is the first carrier disk 403. At the second planet carrier plate 402 'is the second carrier disk 405. To the second

Central opening 420 around an annular portion 437 is arranged. A trough-shaped part 439 of the adapter element is present around the second central opening 420 in an inner region of the planet carrier 401, which may also be referred to as the sun shaft stub area (compared to a plane created by the second carrier disk 405).

In the planetary gear 500 shown in Figures 12 to 15, a planet carrier 401 is installed, which is formed according to Figure 9 with its centrally arranged discharge plate 296 '. A first step planetary gear 502 and a second step planetary gear 506 are mounted in the planetary carrier 401. A ring gear 512 engages the small planets, such as the small planet 504. A differential case 508 is fixed to the planetary carrier 401 with six screws, such as the screw 514 or the screw 514 ¹ . The screws 514, 514 ¹ are equally spaced in pairs and oriented toward the interior 590 (cf., FIG. 15) of the planetary carrier 401 under the jacket sections, such as the jacket section 494.

The central derivation of forces, in particular torsional moments via the planetary carrier 401, can be better understood when the cross-sectional view of the planetary gear 500 in Figure 15 is considered. For better illustration, the ring gear 512 known from FIG. 14 has been omitted in the illustration of FIG.

As can be seen in FIG. 15, around an axial center 498 of the planetary gear 500, coincides with the sun axis 406 of the sun gear 51 1 at the same time, the planet carrier 401 arranged rotationally symmetrical. The sun gear 51 1 forms, together with a hollow shaft stub 540, a one-piece structural unit of the planetary gear 500. The planet carrier 401 is guided on a first ball bearing 520 and a second ball bearing 526. The ball bearings 520, 526 are spaced from the planetary bearing elements, such as the first planetary bearing element 421, in a radial direction toward the center 498. The first bearing 520 is held in an axial direction 560 by the first carrier disk 403 as part of the first planet carrier plate 402. Teeth of the sun gear 51 1 are partially engaged with teeth of the larger planet 503 of the stepped planetary gear 502 partially.

A first needle bearing 530 and a second needle bearing 532 are separated by a ring channel 582 on a lateral surface of the first planetary bearing member 421. In other words, the needle bearings 530, 532 are rotary bearings of the stepped planetary gear 502 on the bolt 421. A lubricant supply to the needle bearings 530, 532 takes place by lubricant, which passes through a lubrication channel 580 in the annular channel 582. A central bore 584 extends in the planetary bearing member 421 to a central region where the lubrication channel 580 branches off from the central bore 584 in a radial direction. From the point of view of the passage of lubricant, just as from the point of view of the transmission of forces, the planetary bearing element 421 may also be referred to as a part of the planetary carrier 401. The needle bearings 530, 532 serve to receive and relay leverage forces that may act on the stepped planetary gear 502. Such forces are forwarded in particular via the planet bearing element 421 to the planet carrier 401. By means of a first center or center outlet 467, which forms a connection via the discharge plate 496 with the second ball bearing 526, the planet carrier 401 is given a particularly high mechanical strength. A possible torsion 550, 552 or a resultant of the torsions 550, 552 is supported on the second ball bearing 526. The first center outlet 467 is bridged over the discharge plate 496 to the bearing seat sleeve 473, which is supported on the second bearing 526. The planet carrier 401 has a receiving region, which can also be referred to as a trough-shaped part 439. The second ball bearing 526 is inserted into the trough-shaped part 439. The bearing seat sleeve 473 encloses the ball bearing 526 in a radial direction. A bearing inner ring 528 of the second ball bearing 526 rests on the hollow shaft stump 540. A bearing seat 471 on the planet carrier 401 forms by its limiting effect a position determination for the ball bearing 526 against an axial direction 560. On the bearing sleeve 439 is provided as an extension in a direction toward the differential housing 508 out an annular region 437, which, in particular in a multi-part planet carrier, can also be referred to as a ring-shaped part. Of the annular region merges into the connecting plate 510, which rests on the carrier disk 405. An air gap 518 is present between the connection plate 510 and the support plate 405. A screw 514, which is screwed into a slug 516, holds the differential housing 508 together with the support plate 405 and the planet carrier plate 402 'via the connection plate 510. The slug 516 projects from the second planet carrier plate 402 ¹ into an inner space 590 of the planetary carrier 401. Between the second planet carrier plate 402 'and the second carrier disk 405, an air gap 518 is present in the assembled state of the transmission 500. The air gap 518 has a favorable effect on a damping of possible resonant vibrations of the planet carrier 401.

16 and 19 show alternative bearings for the planetary bearing ^elements 621, 621 ', 621 ", 621. The planetary gear 700 has a drive wheel 713 and a ring gear 712. The drive wheel 713 drives a sun gear 711 of the planetary gear 700 Webs 602, 602 ^{1 of} the planetary carrier 601 provide the holding and fixing points for the planetary bearing elements 621, 621 ', 621 ", 621 Thus, a planetary bearing element 621 ^{m be} mounted on both sides via ball bearings 734, 736 easily. In this way it is possible to mount the individual gears, but also only individual gears (thus not all, but only some, eg the gears belonging to a stage) by circulation roller bearings on the planet carrier plates. As can be seen from FIG. 18, individual toothed wheels may also be integrally formed with the planetary bearing element, which is supported on the planet carrier via revolving rolling bearings. It can also be said that gear stubs serve for bearing against ball bearings, which bear against the planet carrier.

FIG. 20 shows a transmission 992 which is composed of a plurality of (partial) transmissions 900, 908. The one transmission 900 is a variant of the transmission 100, the planet carrier 1 is presented in more detail in Figures 2 to 8. On the output side, the transmission 900 is followed by a differential 908.

It can also be said that FIG. 20 shows a planetary take-up device as a whole designated 801 for receiving planetary gears 902 for a (total) transmission 992 shown schematically in FIG. 20 in a sectional view, one part of which is a planetary gear 900.

The design options shown in the individual figures can also be interconnected in any form.

So it is also possible, with the same construction principle or after the same Design engineering to realize a double or even a multiple planetary gear.

It is also possible to equip individual gears with involute gears. Summarizing some aspects of the above, the present invention is concerned with a planetary gear and its planet carrier in which, due to center coupling, a first moment and a second moment originating from torsions of the planetary bearing elements on the planet carrier at least partially compensate for each other thanks to favorable merger of moments experienced mutually canceling moments before their removal. This makes it possible, a filigree, z. B. made in sheet metal to use planet carrier for planetary gear with larger torques.

LIST OF REFERENCE NUMBERS

, 1 ', 201, 201', 401, planet carrier

01, 801

02, 402, 602 first planet carrier plate, in particular web

02 ', 202 ", 402', 602 ¹ second planet carrier plate, in particular web

, 3 ', 203, 403 first carrier disk

, 5 ¹ , 205, 405 second carrier disk

, 206, 406 solar axis, in particular sun gear axis

first outer dimension

diameter

second outer dimension

I, 1 1 ', 1 1 "connection opening

2, 12 ', 12 "connection opening

3 support collars

5, 215 collar width

7 stop nose

9, 219 first central opening

0, 220, 420 second central opening

1, 221, 421, 621, first planetary bearing element, in particular first bolt

21 ', 621 ", 621

7 first end of the planetary bearing element, in particular of the bolt 8, 228 first Bolzeneinführöffnung

9 second end of the planetary bearing element, in particular of Bolzens0, 230, 430 second Bolzeneinführöffnung

1, 31 ', 31 "adapter element

2 first middle penetration

3 first rotation

4 second middle penetration

5 second rotation

7, 437 annular part, in particular of the adapter element

8 outer diameter of the adapter element, in particular the

annular part

8 'tray insert opening

9, 39 ', 239, 239 ¹ , 439 trough-shaped part, in particular of the adapter element

0 center area

0 'adapter ring insert area first cover

second cover

first leg of the first cover

second leg of the first cover

third leg of the first cover

first leg of the second cover

second leg of the second cover

third leg of the second cover

first space, in particular the planetary gear second space, in particular the planetary gear first spacer

second spacer

, 265 Total spacers

, 67 ', 267, 267 ¹ , 467 first center outlet, in particular center connection or

mid decoupling

, 269, 269 'second center outlet, in particular center coupling or

mid decoupling

, 471 Bearing seat

, 273, 473 bearing seat sleeve

, 75 'fitting wreath, in particular of the bearing seat

first connection nose

second connection nose

third connection nose

fourth connection nose

first connection opening

fifth connection nose

second connection opening

sixth connection nose

support structure

2 coat, in particular openwork coat

4, 494, 494 'shell portion, in particular arm-like Mantelabschnitt6, 296', 496 discharge plate

8 center

0, 300, 500, 700, planetary gear , 502, 902 first planetary gear, in particular Stufenplanetenzahnrad. 503 bigger planet

, 504 smaller planet

second planetary gear, in particular second step gear, 508, 908 differential, in particular differential housing

Flashing

, 51 1, 711 Sunwheel

, 512, 712 ring gear

Drive wheel, especially for the sun gear, 514 'screw

slugs

air gap

, 520 first bearing, in particular ball bearings

, 526 second bearing, in particular ball bearings

Bearing inner ring

third bearing, in particular first needle bearing

fourth bearing, in particular second needle bearing

first bearing for bolts, in particular ball bearings

second bearing for bolts, in particular ball bearings

Hollow shaft stump, in particular of the sun gear

, 550 first twist

, 552 second twist

Resulting of the torsions

axially

Beölungskanal

annular channel

central bore

inner space

total gear

Claims

claims:

1 . Planetary gear (100, 300, 500, 700, 900) with a planet carrier (1, 1 ¹ , 201, 201 ', 401, 601)

for holding at least one planetary gear (102, 502, 303, 304, 503, 504, 506), in particular at least two adjacent stages, for. B. in the sense of two partial transmission planes,

wherein the planetary gear (102, 502, 303, 304, 503, 504, 506) freely rotatably supports on a gear carrier as a planetary ^{bearing element} , characterized in that the planet ^{bearing element} (21, 421, 621, 621 ', 621 ", 621 ^Ml ), such as a bolt or a shaft-like pin, extending from a first, outer, limiting carrier disk (3, 3 ¹ , 203, 403),

which is configured in particular as a first planet carrier plate or as a web, up to at least one second, outer, limiting carrier disk (5, 5 ¹ , 205,

405)

which is designed in particular as a second planet carrier plate or as a web, preferably via one, in particular torsions (150, 152, 154, 550, 552) via the planet ^{bearing element} (21, 421, 621, 621 ', 621 ", 621 ^Ml ) dissipative, Discharge plate (296, 296 ', 496),

which optionally forms a cover (41, 43) extends

and or

a first torque in the first carrier disk (3, 3 ¹ , 203, 403) and a second torque in the second carrier disk (5, 5 ¹ , 205, 405) on a center coupling (67, 67 ¹ , 267, 267 ¹ , 467, 69, 269, 269 ¹ ) guided on a, in particular stationary, component, such as a continuing component (108, 508), z. B. a further transmission component and / or a torque-conducting part, are discharged.

2. planetary gear (100, 300, 500, 700, 900) according to claim 1,

characterized in that

arms, jacket sections (294, 494, 494 ¹ ), legs (45, 47, 49, 51, 53, 55) or arm-like extensions protrude laterally from the deflector plate (296, 496),

z. B. alternately extending in two opposite directions,

which preferably extend to the carrier disks (3, 3 ', 203, 403, 5, 5 ¹ , 205, 405).

3. planetary gear (100, 300, 500, 700, 900) according to one of the preceding claims, characterized in that

the planet carrier (1, 1 ', 201, 201', 401, 601) is a segmented hollow cylinder with a, in particular at least partially perforated, jacket,

wherein preferably the support discs (3, 3 ', 203, 403, 5, 5 ¹ , 205, 405) to each other via arm-like shell portions (45, 47, 49, 51, 53, 55), such as arms, are held in a spaced manner.

4. planetary gear (100, 300, 500, 700, 900) according to one of the preceding claims, characterized in that

a moment in the planetary carrier (1, 1 ^1, 201, 201 ', 401, 601) about a center (498) of the planet carrier (1, 1', 201, 201 ', 401, 601),

preferably in a central position of the planet carrier (1, 1 ', 201, 201', 401, 601), is deflected.

5. planetary gear (100, 300, 500, 700, 900),

in particular according to one of the preceding claims,

characterized in that

the carrier disks (3, 3 ', 203, 403, 5, 5 ¹ , 205, 405) of a planetary carrier (1, 1 ¹ , 201, 201', 401, 601) are decoupled from an abortive component (108) of a drive train to the planetary carrier abortive component via a Mittenausleitung (67, 67 ', 69), such as. B. an adapter element (31, 31 ', 31 "), are connected, for example, over slugs.

6. planetary gear (100, 300, 500, 700, 900) according to one of the preceding claims, characterized in that

it is configured for a torque transmission from a sun gear to a respective larger planet of each two planets comprehensive planets (102), so that smaller planets of the stepped planetary can mesh on a ring gear.

7. planetary gear (100, 300, 500, 700, 900) according to one of the preceding claims, characterized in that

a bolt for a planet (102) laterally on the discharge plate (296, 496) over in one piece from a carrier disk (3, 3 ¹ ) to a next carrier disk (5, 5 ¹ ) extends.

8. planetary gear (100, 300, 500, 700, 900) according to one of the preceding claims, characterized in that a rigidity of the first carrier disc (3, 3 ¹ ) and a stiffness of the second carrier disc (5, 5 ¹ ) are equal.

9. planetary gear (100, 300, 500, 700, 900) according to one of the preceding claims, characterized in that

each carrier disc (3, 3 ', 203, 403, 5, 5 ¹ , 205, 405) is torsionsverwindungsfrei, in particular an introductory torque and an expelling torque of the planet (102) by tangential discharge via a bearing seat sleeve mutually canceling contribute to Torsionsverwindungsfreiheit ,

10. Planetary gear (100, 300, 500, 700, 900) according to one of claims 6 to 9,

characterized in that

a coupling in alignment between gears of the stepped planet (102) for a torque-based discharge of moments in the carrier disks (3, 3 ¹ , 203, 403, 5, 5 ¹ , 205, 405) on a, in particular stationary, element, such as a

Connecting plate (510) to a differential (108, 508), is provided.

1 1. measure for supporting planets (102, 303, 304, 502, 503, 504, 506) of a planetary gear (100, 300, 500, 700, 900),

in particular according to one of the preceding claims,

at the planet (102, 303, 304, 502, 503, 504, 506), such. B. stepped planets on planetary bearing elements such. B. a bolt or a wave-like pin, are arranged,

which in carrier disks or webs of a planet carrier (1, 1 ¹ , 201, 201 ', 401, 601) are fastened, characterized in that a first torque in a first carrier disk and a second torque in a second carrier disk guided on a center coupling on a, preferably stationary, component are discharged,

in particular, while an independent torque flow between a sun gear, the planets or step planets and a ring gear takes place.